US20070000480A1 - Fuel injecton valve - Google Patents
Fuel injecton valve Download PDFInfo
- Publication number
- US20070000480A1 US20070000480A1 US10/566,534 US56653404A US2007000480A1 US 20070000480 A1 US20070000480 A1 US 20070000480A1 US 56653404 A US56653404 A US 56653404A US 2007000480 A1 US2007000480 A1 US 2007000480A1
- Authority
- US
- United States
- Prior art keywords
- fuel injector
- seal
- recited
- fuel
- nozzle body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 71
- 238000002485 combustion reaction Methods 0.000 claims abstract description 21
- 238000002347 injection Methods 0.000 claims abstract description 9
- 239000007924 injection Substances 0.000 claims abstract description 9
- 230000004323 axial length Effects 0.000 claims abstract description 3
- 239000002826 coolant Substances 0.000 claims description 2
- 239000011888 foil Substances 0.000 claims description 2
- 239000002184 metal Substances 0.000 claims description 2
- 238000007789 sealing Methods 0.000 description 10
- 238000009434 installation Methods 0.000 description 5
- 238000004939 coking Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 239000004020 conductor Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000013536 elastomeric material Substances 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
- F02M53/04—Injectors with heating, cooling, or thermally-insulating means
Definitions
- the present invention relates to a fuel injector for direct injection of fuel, which fuel injector is provided with a seal.
- a fuel injector for the direct injection of fuel into the combustion chamber of a mixture-compressing internal combustion engine having external ignition includes a valve housing formed by a nozzle body, and a sealing ring which seals the fuel injector from a cylinder head of the internal combustion engine.
- the sealing ring has a convexly arched profile, the two ends of the sealing ring axially overlapping in the form of a step.
- the fuel injector according to the present invention has the advantage that a seal is situated between the cylinder head and the nozzle body, the seal extending over the entire axial length and having a suitable structure, thereby providing not only a reliable sealing effect but effective heat dissipation away from the nozzle body as well.
- any desired cross sections are possible, e.g., corrugated tubes, convoluted bellows, and smooth tubular bodies having protuberances formed in a variety of shapes.
- the seal may also be made up of a plurality of layers, which gives it higher stability and makes it less likely to be damaged during the installation.
- a cover plate which functions as heat shield, may be situated on a discharge-side end of the seal.
- the cover plate may have an opening for the spray-discharged fuel jets or it may have a plurality of spray-discharge openings.
- the seal may be produced from a metallic material having an amorphous structure, so that a smooth surface is able to be achieved.
- FIG. 1 shows a schematic cross-sectional view through a conventional fuel injector.
- FIG. 2 shows a schematic cross-sectional view of a first example embodiment of a fuel injector according to the present invention.
- FIG. 3 shows a schematic cross-sectional view of a second example embodiment of a fuel injector according to the present invention.
- FIG. 4 shows a schematic cross-sectional view of a third example embodiment of a fuel injector according to the present invention.
- FIG. 5 shows a schematic cross-sectional view of a fourth example embodiment of a fuel injector according to the present invention.
- FIG. 6 shows a schematic cross-sectional view of a fifth example embodiment of a fuel injector according to the present invention.
- FIG. 7 shows a schematic cross-sectional view of a sixth example embodiment of a fuel injector according to the present invention.
- Fuel injector 1 is configured for fuel-injection systems of mixture-compressing internal combustion engines with externally supplied ignition. Fuel injector 1 is suited, e.g., for the direct injection of fuel into a combustion chamber 2 of an internal combustion engine.
- Fuel injector 1 includes a nozzle body 3 , which is sealed from a cylinder head 5 of the internal combustion engine by a sealing ring 4 .
- Sealing ring 4 is made of, for instance, an elastomeric material such as a Teflon-coated material and provides the sealing effect in cylinder head 5 as a result of a slightly larger diameter compared to nozzle body 3 .
- fuel injector 1 includes a housing 6 , an electric plug-in contact 7 for actuating fuel injector 1 , and a fuel feed 8 , via which the fuel is conveyed.
- Fuel may be supplied via a fuel-distributor line, for example, which is not shown further.
- Disadvantages of the sealing rings 4 in the conventional configuration is, in particular, the poor heat transfer between nozzle body 3 and cylinder head 5 because of an air gap 9 on the discharge side between fuel injector 1 and cylinder head 5 .
- the lowest possible temperature is to be desired in the region of the valve tip. This prevents a complete evaporation of the fuel remaining in the region of the valve tip after the injection process. If the fuel remains liquid, the combustion residue and impurities are unable to deposit in the region of the valve tip and are carried away during the next injection cycle.
- Seals 10 are made of a material that exhibits great thermal conductivity, e.g., a metal foil having an amorphous structure, so that it is possible to achieve a very smooth surface with the advantage of a simple and damage-free installation.
- Cavities 16 formed between fuel injector 1 and seal 10 by the different cross-sectional forms may be used for passing through a coolant.
- fuel injectors 1 provided with corresponding seals 10 will be described.
- fuel injectors 1 according to the present invention may be designed similar to the conventional fuel injector illustrated in FIG. 1 .
- FIG. 2 shows a first example embodiment of a fuel injector 1 configured according to the present invention.
- seal 10 has the form of a corrugated tube. Seal 10 is open at both sides and is thus able to be mounted in an especially uncomplicated manner. Seal 10 may be premounted on nozzle body 3 of fuel injector 1 and then inserted into cylinder head 5 together with it.
- FIG. 3 shows a second example embodiment of a fuel injector 1 configured according to the present invention.
- seal 10 has the form of a tubular seal 10 having protrusions 11 .
- Protrusions 11 are approximately semicircular in section.
- the advantage of this embodiment is a slightly larger contact surface on nozzle body 3 resulting in improved thermal conductivity.
- FIG. 4 shows a third example embodiment of a fuel injector 1 configured according to the present invention.
- seal 10 has a pleated design and has been formed into expansion bellows 10 .
- the thermal conductivity and sealing ability correspond approximately to that of the first example embodiment described in FIG. 2 .
- FIG. 5 shows a fourth example embodiment of a fuel injector 1 configured according to the present invention.
- seal 10 is made up of a plurality of layers 12 in a sandwich-like manner. This increases the durability of seal 10 , in particular, which is unable to deform as easily during installation and thus is less likely to be damaged.
- the individual layers 12 may in turn be designed in the form of a corrugated-tube and be bonded to each other, or they may be joined to each other only at their ends.
- FIG. 6 shows a fifth example embodiment of a fuel injector 1 configured according to the present invention.
- seal 10 may have the same cross-sectional design as seals 10 according to the example embodiments illustrated in FIGS. 2 through 5 , the corrugated tube design having been chosen in FIG. 6 .
- cover plate 14 which has an opening 15 for the fuel jets injected into combustion chamber 2 from at least one spray-discharge orifice of fuel injector 1 .
- Cover plate 14 additionally has the function of a heat shield and protects the spray-discharge orifices from the high temperature prevailing in the combustion chamber, the high temperatures increasing the coking tendency of the spray-discharge orifices.
- FIG. 7 shows a sixth example embodiment of a fuel injector 1 configured according to the present invention.
- seal 10 may have the same sectional design as seals 10 illustrated in FIGS. 2 through 5 , the corrugated tube design having been chosen in FIG. 7 as well.
- Seal 10 has a cover plate 14 on a discharge-side end 13 , into which the spray-discharge orifices may be worked directly. Cover plate 14 also assumes the function of a heat shield and protects the discharge-side end of fuel injector 1 from the temperature prevailing in the combustion chamber.
- the present invention is not restricted to the example embodiments shown, but is also applicable to other cross-sectional forms of seals 10 , as well as to a wide variety of construction types of fuel injectors 1 , such as fuel injectors 1 having an interface to an intake manifold or a common-rail system.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
- The present invention relates to a fuel injector for direct injection of fuel, which fuel injector is provided with a seal.
- Published European patent document EP 0 828 075 describes a fuel injector for the direct injection of fuel into the combustion chamber of an internal combustion engine, which has a device for adjusting the temperature in the region of the valve tip so as to reduce deposits in this area. The device is embodied in the form of a coating made of a thermally conductive material on the valve tip.
- Disadvantages of the fuel injector described in the European patent document EP 0 828 075 are the high demands regarding the accuracy of fit of the components and the complicated installation, which is involved and thus cost-intensive.
- Furthermore, a fuel injector for the direct injection of fuel into the combustion chamber of a mixture-compressing internal combustion engine having external ignition is described in published German patent document DE 101 09 407. It includes a valve housing formed by a nozzle body, and a sealing ring which seals the fuel injector from a cylinder head of the internal combustion engine. The sealing ring has a convexly arched profile, the two ends of the sealing ring axially overlapping in the form of a step.
- Particularly disadvantageous in the fuel injector described in published German patent document DE 101 09 407 is the air gap between the fuel injector and the cylinder head, which allows only limited heat transfer. This is disadvantageous in reducing deposits on the valve tip since the temperature in the region of the spray-discharge orifices must be as low as possible so as to avoid deposits.
- In contrast, the fuel injector according to the present invention has the advantage that a seal is situated between the cylinder head and the nozzle body, the seal extending over the entire axial length and having a suitable structure, thereby providing not only a reliable sealing effect but effective heat dissipation away from the nozzle body as well.
- It is particularly advantageous that any desired cross sections are possible, e.g., corrugated tubes, convoluted bellows, and smooth tubular bodies having protuberances formed in a variety of shapes.
- In an advantageous manner the seal may also be made up of a plurality of layers, which gives it higher stability and makes it less likely to be damaged during the installation.
- In addition, it is advantageous that a cover plate, which functions as heat shield, may be situated on a discharge-side end of the seal. The cover plate may have an opening for the spray-discharged fuel jets or it may have a plurality of spray-discharge openings.
- The seal may be produced from a metallic material having an amorphous structure, so that a smooth surface is able to be achieved.
-
FIG. 1 shows a schematic cross-sectional view through a conventional fuel injector. -
FIG. 2 shows a schematic cross-sectional view of a first example embodiment of a fuel injector according to the present invention. -
FIG. 3 shows a schematic cross-sectional view of a second example embodiment of a fuel injector according to the present invention. -
FIG. 4 shows a schematic cross-sectional view of a third example embodiment of a fuel injector according to the present invention. -
FIG. 5 shows a schematic cross-sectional view of a fourth example embodiment of a fuel injector according to the present invention. -
FIG. 6 shows a schematic cross-sectional view of a fifth example embodiment of a fuel injector according to the present invention. -
FIG. 7 shows a schematic cross-sectional view of a sixth example embodiment of a fuel injector according to the present invention. - Before example embodiments of a
fuel injector 1 according to the present invention are described in greater detail in connection withFIGS. 2 through 7 , for a better understanding of the present invention, aconventional fuel injector 1 will be briefly explained in terms of its essential components on the basis ofFIG. 1 . -
Fuel injector 1 is configured for fuel-injection systems of mixture-compressing internal combustion engines with externally supplied ignition.Fuel injector 1 is suited, e.g., for the direct injection of fuel into acombustion chamber 2 of an internal combustion engine. -
Fuel injector 1 includes anozzle body 3, which is sealed from acylinder head 5 of the internal combustion engine by a sealing ring 4. Sealing ring 4 is made of, for instance, an elastomeric material such as a Teflon-coated material and provides the sealing effect incylinder head 5 as a result of a slightly larger diameter compared tonozzle body 3. - Furthermore,
fuel injector 1 includes ahousing 6, an electric plug-in contact 7 for actuatingfuel injector 1, and afuel feed 8, via which the fuel is conveyed. Fuel may be supplied via a fuel-distributor line, for example, which is not shown further. - Disadvantages of the sealing rings 4 in the conventional configuration is, in particular, the poor heat transfer between
nozzle body 3 andcylinder head 5 because of anair gap 9 on the discharge side betweenfuel injector 1 andcylinder head 5. In order to counter the threat of coking of the spray-discharge orifices of directly-injectingfuel injectors 1 as a result of the high temperatures incombustion chamber 2, the lowest possible temperature is to be desired in the region of the valve tip. This prevents a complete evaporation of the fuel remaining in the region of the valve tip after the injection process. If the fuel remains liquid, the combustion residue and impurities are unable to deposit in the region of the valve tip and are carried away during the next injection cycle. - The poor heat transfer between
fuel injector 1 andcylinder head 5 in the conventional configuration is counteracted by aseal 10 configured according to the present invention, as illustrated by example embodiments shown inFIGS. 2 through 7 . -
Seals 10 described below all have in common the fact that they are designed as corrugated tubes and thus not only provide excellent sealing action but also offer a sufficiently large contact surface for an effective heat transfer betweenfuel injector 1 andcylinder head 5.Seals 10 are designed in such a way that they are short and broad in the non-installed state, but are pressed together slightly by the installation and become longer as a result. This makes it possible to achieve an excellent fit. -
Seals 10 are made of a material that exhibits great thermal conductivity, e.g., a metal foil having an amorphous structure, so that it is possible to achieve a very smooth surface with the advantage of a simple and damage-free installation. -
Cavities 16 formed betweenfuel injector 1 andseal 10 by the different cross-sectional forms may be used for passing through a coolant. - In the following, example embodiments for
fuel injectors 1 provided withcorresponding seals 10 will be described. With the exception of the inventive measures provided according to the present invention,fuel injectors 1 according to the present invention may be designed similar to the conventional fuel injector illustrated inFIG. 1 . -
FIG. 2 shows a first example embodiment of afuel injector 1 configured according to the present invention. Here, in the simplest manner,seal 10 has the form of a corrugated tube.Seal 10 is open at both sides and is thus able to be mounted in an especially uncomplicated manner.Seal 10 may be premounted onnozzle body 3 offuel injector 1 and then inserted intocylinder head 5 together with it. -
FIG. 3 shows a second example embodiment of afuel injector 1 configured according to the present invention. In this example embodiment,seal 10 has the form of atubular seal 10 havingprotrusions 11.Protrusions 11 are approximately semicircular in section. The advantage of this embodiment is a slightly larger contact surface onnozzle body 3 resulting in improved thermal conductivity. -
FIG. 4 shows a third example embodiment of afuel injector 1 configured according to the present invention. In thiscase seal 10 has a pleated design and has been formed intoexpansion bellows 10. The thermal conductivity and sealing ability correspond approximately to that of the first example embodiment described inFIG. 2 . -
FIG. 5 shows a fourth example embodiment of afuel injector 1 configured according to the present invention. Here,seal 10 is made up of a plurality oflayers 12 in a sandwich-like manner. This increases the durability ofseal 10, in particular, which is unable to deform as easily during installation and thus is less likely to be damaged. Theindividual layers 12 may in turn be designed in the form of a corrugated-tube and be bonded to each other, or they may be joined to each other only at their ends. -
FIG. 6 shows a fifth example embodiment of afuel injector 1 configured according to the present invention. Here,seal 10 may have the same cross-sectional design asseals 10 according to the example embodiments illustrated inFIGS. 2 through 5 , the corrugated tube design having been chosen inFIG. 6 . In addition, on a discharge-side end 13, it is provided with acover plate 14 which has anopening 15 for the fuel jets injected intocombustion chamber 2 from at least one spray-discharge orifice offuel injector 1.Cover plate 14 additionally has the function of a heat shield and protects the spray-discharge orifices from the high temperature prevailing in the combustion chamber, the high temperatures increasing the coking tendency of the spray-discharge orifices. -
FIG. 7 shows a sixth example embodiment of afuel injector 1 configured according to the present invention. Here, as in the example embodiment shown inFIG. 6 , seal 10 may have the same sectional design asseals 10 illustrated inFIGS. 2 through 5 , the corrugated tube design having been chosen inFIG. 7 as well.Seal 10 has acover plate 14 on a discharge-side end 13, into which the spray-discharge orifices may be worked directly.Cover plate 14 also assumes the function of a heat shield and protects the discharge-side end offuel injector 1 from the temperature prevailing in the combustion chamber. - The present invention is not restricted to the example embodiments shown, but is also applicable to other cross-sectional forms of
seals 10, as well as to a wide variety of construction types offuel injectors 1, such asfuel injectors 1 having an interface to an intake manifold or a common-rail system. - In addition, the individual features of the various example embodiments may be combined with each other as desired.
Claims (13)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10337892A DE10337892A1 (en) | 2003-08-18 | 2003-08-18 | Fuel injector |
DE10337892.8 | 2003-08-18 | ||
PCT/EP2004/051820 WO2005019640A1 (en) | 2003-08-18 | 2004-08-18 | Fuel injection valve |
Publications (2)
Publication Number | Publication Date |
---|---|
US20070000480A1 true US20070000480A1 (en) | 2007-01-04 |
US7261089B2 US7261089B2 (en) | 2007-08-28 |
Family
ID=34201626
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/566,534 Expired - Fee Related US7261089B2 (en) | 2003-08-18 | 2004-08-18 | Fuel injector nozzle seal |
Country Status (5)
Country | Link |
---|---|
US (1) | US7261089B2 (en) |
EP (1) | EP1658428B8 (en) |
JP (1) | JP4537398B2 (en) |
DE (2) | DE10337892A1 (en) |
WO (1) | WO2005019640A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7334571B1 (en) * | 2006-08-31 | 2008-02-26 | Gm Global Technology Operations, Inc. | Isolation system for high pressure spark ignition direct injection fuel delivery components |
US20080264390A1 (en) * | 2005-02-14 | 2008-10-30 | Klaus Rottenwohrer | Injection Valve for Injecting Fuel and Cylinder Head |
US20110068194A1 (en) * | 2008-12-11 | 2011-03-24 | Mitsubishi Heavy Industries, Ltd. | Cooling structure of fuel injection valve |
US20130311062A1 (en) * | 2012-05-21 | 2013-11-21 | Ford Global Technologies, Llc | Engine system and a method of operating a direct injection engine |
WO2019072683A1 (en) * | 2017-10-12 | 2019-04-18 | Continental Automotive Gmbh | Fuel injection valve |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10354465B4 (en) * | 2003-11-21 | 2014-07-17 | Robert Bosch Gmbh | Fuel injector |
DE102006009094A1 (en) * | 2006-02-28 | 2007-08-30 | Bayerische Motoren Werke Ag | Damper for use between cylinder head and injector in region of injector foot, has sub-functional section e.g. inner ring and outer ring, for fixing injector with respect to cylinder head, where damper is formed as multipart structure |
FR2906576B1 (en) * | 2006-10-03 | 2011-03-04 | Renault Sas | COOLING ARRANGEMENT OF AN INJECTOR COMPRISING A WASHER STACK. |
FR2907854B1 (en) * | 2006-10-25 | 2008-12-26 | Renault Sas | COOLING ARRANGEMENT OF AN INJECTOR COMPRISING TWO BITTER SPRINGS IN EACH OTHER |
US7406946B1 (en) * | 2007-04-02 | 2008-08-05 | Hitachi, Ltd. | Method and apparatus for attenuating fuel pump noise in a direct injection internal combustion chamber |
US7527038B2 (en) * | 2007-04-02 | 2009-05-05 | Hitachi, Ltd | Method and apparatus for attenuating fuel pump noise in a direct injection internal combustion chamber |
US20110303192A1 (en) * | 2007-05-02 | 2011-12-15 | Klaus Jung | Internal combustion engine with sealing protection for a fuel injection valve |
US7513242B2 (en) * | 2007-05-03 | 2009-04-07 | Cummins Inc. | Fuel injector assembly with injector seal retention |
DE102009029088A1 (en) * | 2009-09-02 | 2011-03-03 | Robert Bosch Gmbh | Fuel injection arrangement with optimized thermal coupling between the fuel injector and the cylinder head |
WO2011038091A2 (en) * | 2009-09-23 | 2011-03-31 | Cummins Intellectual Properties, Inc. | Injector seal assembly and method of sealing a coolant passage from an injector |
US9382887B2 (en) | 2009-09-23 | 2016-07-05 | Cummins Intellectual Property. Inc. | Engine component seal assembly and method of sealing a coolant passage from an engine component |
US20150059322A1 (en) * | 2013-08-30 | 2015-03-05 | Continental Automotive Systems, Inc. | Liquid cooled reductant delivery unit for automotive selective catalytic reduction systems |
US9453486B1 (en) * | 2015-03-20 | 2016-09-27 | Continental Automotive Systems, Inc. | Gas direct injector with reduced leakage |
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US4589596A (en) * | 1980-01-03 | 1986-05-20 | Robert Bosch Gmbh | Nozzle for internal combustion engines |
US5129658A (en) * | 1990-03-02 | 1992-07-14 | Procal | Seal for an internal combustion engine injector |
US5381600A (en) * | 1993-10-06 | 1995-01-17 | Ford Motor Company | Heat exchanger and method of making the same |
US6009856A (en) * | 1998-05-27 | 2000-01-04 | Caterpillar Inc. | Fuel injector isolation |
US6295969B1 (en) * | 1998-11-13 | 2001-10-02 | Sanshin Kogyo Kabushiki Kaisha | Injector mounting arrangement for direct-injected engines |
US6481421B1 (en) * | 1999-12-24 | 2002-11-19 | Robert Bosch Gmbh | Compensating element |
US6578554B2 (en) * | 2001-01-12 | 2003-06-17 | Ford Global Technologies, Llc | Fuel injection arrangement |
US7047949B2 (en) * | 2003-06-27 | 2006-05-23 | Siemens Ag | Venting device |
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GB730432A (en) * | 1952-05-17 | 1955-05-25 | Maschf Augsburg Nuernberg Ag | Improvements in and relating to fuel injection internal combustion engines |
JPH1089192A (en) | 1996-09-10 | 1998-04-07 | Toyota Central Res & Dev Lab Inc | Deposit reducing-type fuel injection valve |
DE19955896A1 (en) * | 1999-11-20 | 2001-05-31 | Daimler Chrysler Ag | Fuel injection jet for internal combustion engine, with push-out path of deflector bush on jet neck limited by stop at transition from annular cavity to annular gap |
DE10109407A1 (en) | 2001-02-28 | 2002-09-05 | Bosch Gmbh Robert | Fuel injector |
-
2003
- 2003-08-18 DE DE10337892A patent/DE10337892A1/en not_active Withdrawn
-
2004
- 2004-08-18 JP JP2006523635A patent/JP4537398B2/en not_active Expired - Fee Related
- 2004-08-18 EP EP04766521A patent/EP1658428B8/en not_active Not-in-force
- 2004-08-18 US US10/566,534 patent/US7261089B2/en not_active Expired - Fee Related
- 2004-08-18 WO PCT/EP2004/051820 patent/WO2005019640A1/en active IP Right Grant
- 2004-08-18 DE DE502004005519T patent/DE502004005519D1/en active Active
Patent Citations (8)
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US4589596A (en) * | 1980-01-03 | 1986-05-20 | Robert Bosch Gmbh | Nozzle for internal combustion engines |
US5129658A (en) * | 1990-03-02 | 1992-07-14 | Procal | Seal for an internal combustion engine injector |
US5381600A (en) * | 1993-10-06 | 1995-01-17 | Ford Motor Company | Heat exchanger and method of making the same |
US6009856A (en) * | 1998-05-27 | 2000-01-04 | Caterpillar Inc. | Fuel injector isolation |
US6295969B1 (en) * | 1998-11-13 | 2001-10-02 | Sanshin Kogyo Kabushiki Kaisha | Injector mounting arrangement for direct-injected engines |
US6481421B1 (en) * | 1999-12-24 | 2002-11-19 | Robert Bosch Gmbh | Compensating element |
US6578554B2 (en) * | 2001-01-12 | 2003-06-17 | Ford Global Technologies, Llc | Fuel injection arrangement |
US7047949B2 (en) * | 2003-06-27 | 2006-05-23 | Siemens Ag | Venting device |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080264390A1 (en) * | 2005-02-14 | 2008-10-30 | Klaus Rottenwohrer | Injection Valve for Injecting Fuel and Cylinder Head |
US7334571B1 (en) * | 2006-08-31 | 2008-02-26 | Gm Global Technology Operations, Inc. | Isolation system for high pressure spark ignition direct injection fuel delivery components |
US20080053409A1 (en) * | 2006-08-31 | 2008-03-06 | Beardmore John M | Isolation system for high pressure spark ignition direct injection fuel delivery components |
US20110068194A1 (en) * | 2008-12-11 | 2011-03-24 | Mitsubishi Heavy Industries, Ltd. | Cooling structure of fuel injection valve |
US20130311062A1 (en) * | 2012-05-21 | 2013-11-21 | Ford Global Technologies, Llc | Engine system and a method of operating a direct injection engine |
US9441569B2 (en) * | 2012-05-21 | 2016-09-13 | Ford Global Technologies, Llc | Engine system and a method of operating a direct injection engine |
WO2019072683A1 (en) * | 2017-10-12 | 2019-04-18 | Continental Automotive Gmbh | Fuel injection valve |
Also Published As
Publication number | Publication date |
---|---|
DE502004005519D1 (en) | 2007-12-27 |
US7261089B2 (en) | 2007-08-28 |
DE10337892A1 (en) | 2005-03-17 |
EP1658428A1 (en) | 2006-05-24 |
JP4537398B2 (en) | 2010-09-01 |
JP2007502931A (en) | 2007-02-15 |
EP1658428B1 (en) | 2007-11-14 |
WO2005019640A1 (en) | 2005-03-03 |
EP1658428B8 (en) | 2008-01-23 |
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